WO1999026755A2 - Dispositif de centrage actif possedant un capteur de charge de cisaillement et un organe de commande encastres - Google Patents

Dispositif de centrage actif possedant un capteur de charge de cisaillement et un organe de commande encastres Download PDF

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Publication number
WO1999026755A2
WO1999026755A2 PCT/US1998/023112 US9823112W WO9926755A2 WO 1999026755 A2 WO1999026755 A2 WO 1999026755A2 US 9823112 W US9823112 W US 9823112W WO 9926755 A2 WO9926755 A2 WO 9926755A2
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WO
WIPO (PCT)
Prior art keywords
workpiece
actuator
center
machine
tip
Prior art date
Application number
PCT/US1998/023112
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English (en)
Other versions
WO1999026755A3 (fr
Inventor
Gordon Douglas Cook
Richard Andrew Daley
Original Assignee
Edo Western Corporation
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Edo Western Corporation filed Critical Edo Western Corporation
Priority to AU12073/99A priority Critical patent/AU1207399A/en
Publication of WO1999026755A2 publication Critical patent/WO1999026755A2/fr
Publication of WO1999026755A3 publication Critical patent/WO1999026755A3/fr

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B24—GRINDING; POLISHING
    • B24B—MACHINES, DEVICES, OR PROCESSES FOR GRINDING OR POLISHING; DRESSING OR CONDITIONING OF ABRADING SURFACES; FEEDING OF GRINDING, POLISHING, OR LAPPING AGENTS
    • B24B5/00—Machines or devices designed for grinding surfaces of revolution on work, including those which also grind adjacent plane surfaces; Accessories therefor
    • B24B5/02—Machines or devices designed for grinding surfaces of revolution on work, including those which also grind adjacent plane surfaces; Accessories therefor involving centres or chucks for holding work
    • B24B5/04—Machines or devices designed for grinding surfaces of revolution on work, including those which also grind adjacent plane surfaces; Accessories therefor involving centres or chucks for holding work for grinding cylindrical surfaces externally
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B24—GRINDING; POLISHING
    • B24B—MACHINES, DEVICES, OR PROCESSES FOR GRINDING OR POLISHING; DRESSING OR CONDITIONING OF ABRADING SURFACES; FEEDING OF GRINDING, POLISHING, OR LAPPING AGENTS
    • B24B49/00—Measuring or gauging equipment for controlling the feed movement of the grinding tool or work; Arrangements of indicating or measuring equipment, e.g. for indicating the start of the grinding operation
    • B24B49/16—Measuring or gauging equipment for controlling the feed movement of the grinding tool or work; Arrangements of indicating or measuring equipment, e.g. for indicating the start of the grinding operation taking regard of the load

Definitions

  • the present invention relates to an active centering apparatus, particularly suitable for use in cylindrical grinding machines and the like, for sensing force levels and vibrational frequencies and for providing force and displacement compensation.
  • the present invention relates to an active centering apparatus having an imbedded shear load sensor and an imbedded actuator.
  • Machining operations such as cylindrical grinding, generate undesirable force levels and vibrational frequencies between the workpiece and the machine tool. These force levels and vibrational frequencies have a detrimental effect on surface finishes, precision tolerances, and cycle times.
  • a harmonic disturbance force causes a periodic motion between a grinding wheel and the workpiece.
  • the periodic motion causes the workpiece to develop a wavy shape.
  • the periodic motion may be caused by grinding wheel imbalance, bearing vibration, motor vibration, etc.
  • Older machines still in use today, operate slowly and are difficult to adjust. For example, retracting the grinding wheel after finishing is slow due to the mass of the grinding wheel and spindle assembly and the use of conventional hydraulic pistons. The slow retraction decreases the quality of the surface finish and increases cycle times. As another example, . a misalignment often exists between the workpiece and the grinding wheel, resulting in a taper in the finished workpiece. Correcting for machine misalignment is a time consuming labor intensive technique.
  • U.S. Patent 5,054,244, issued October 8, 1991 to Takamatsu et al. discloses a polishing apparatus with a rotating polishing tool applied to a workpiece held by a movable table.
  • a load cell or strain gauge is disposed under the table for detecting an applied tool force.
  • the load cell generates a signal which is sent to a controller.
  • the controller generates a signal which is sent to a piezoelectric member, also disposed under the table, which moves the table in response to the workpiece.
  • U.S. Patent 4,590,573, issued May 20, 1986 to Hahn discloses a grinding machine with a workpiece rotatably mounted to a workhead, which in turn is mounted on a base, and an abrasive tool rotatably mounted to a wheelhead.
  • the wheelhead is mounted to a table, which in turn is movably mounted on the base.
  • a feed means moves the tool and wheelhead on the base with respect to the workpiece and workhead.
  • a sensor is disposed on the wheelhead for sensing grinding force. The sensor generates a signal which is sent to a controller. The controller, in turn, generates a signal which is sent to the feed means to move the table, and thus the wheelhead and tool .
  • U.S. Patent 4,602,459 issued July 29, 1986 to Drits et al. discloses a hinged table holding a workpiece against a grinding wheel.
  • a sensor is disposed under the table for sensing the position of the table.
  • the sensor generates a signal which is sent to a controller.
  • the controller generates a signal which is sent to a piezoelectric actuator to pivot the table, and thus the workpiece, with respect to the grinding wheel.
  • Some of the above devices require special tables to transmit the force or displacement applied by the tool to a sensor and to transmit the force and displacement applied by the actuation to the workpiece. All the above devices respond by activating an actuator to move a table and cause relative movement between the workpiece and a tool. None of the above devices address cylindrical grinding machines or similar machines that support the workpiece between spindles or centers.
  • a device capable of sensing and/or responding to undesirable force levels and vibrational frequencies. It also would be advantageous to develop such a device capable of being used with existing machines without extensive retro-fitting. It also would be advantageous to develop such a device for providing real-time force measurement without disturbing the work space in order to determine undesirable force levels and frequencies. It also would be advantageous to develop such a device capable of adjusting for relative taper between the workpiece and the tool. In addition, it would be advantageous to develop such a device capable of rapidly removing the workpiece from the tool.
  • an active center device having an imbedded shear load sensor and an imbedded piezoelectric actuator.
  • the shear load sensor senses force levels and vibrational frequencies generated between the workpiece and the grinding wheel.
  • the sensor develops a sensor signal and supplies the signal to a controller.
  • the piezoelectric actuator includes a pair of piezoelectric stacks disposed on opposing sides of the center body.
  • the stacks are disposed in a pair of indentations also formed in opposing sides of the center body.
  • a web is formed between the pair of indentations.
  • the piezoelectric stacks are responsive to control signals developed and supplied by the controller. The signals cause the stacks to expand and contract. Because the piezoelectric stacks are contained in the indentations, their expansion and contraction causes the center body to bend. Because the center is fixed in a stock, the tip of the center bends about the web. Thus, the actuators cause the tip to displace laterally and apply a lateral force to the workpiece.
  • the controller monitors the characteristics of the cylindrical grinding machine and compensates for changes. Thus, the controller can calibrate the grinding machine set-up and adjust performance. The result is better surface finishes and faster throughput.
  • the controller may supply an AC voltage waveform to the actuators to provide force control.
  • the controller may also supply a DC voltage to cause a known displacement of the tip.
  • the workpiece may be rapidly removed from the grinding wheel for better surface finish and faster through-put.
  • the workpiece may be adjusted with respect to the grinding wheel to correct for misalignment.
  • the workpiece may be adjusted radially, during the grinding operation, to produce a contoured pattern along the circumferential surface of the workpiece .
  • FIG. 1 is a schematic view of a preferred embodiment of an apparatus for use with cylindrical grinding having active centers in accordance with the principles of the present invention.
  • FIG. 2 is a top view of a preferred embodiment of the active centers of the present invention installed on a cylindrical grinding machine.
  • FIG. 3 is a perspective view of a preferred embodiment of the active center of the present invention with a piezoelectric stack exposed.
  • FIG. 4 is a top view of a preferred embodiment of an active center of the present invention.
  • FIG. 5 is a top view of a preferred embodiment of the active center with the movement of the tip shown in dashed lines .
  • FIG. 6 is a perspective view of a preferred embodiment of a piezoelectric stack of the present invention.
  • FIG. 7 is a perspective view of an alternative embodiment of a piezoelectric stack of the present invention.
  • FIG. 8 is a cross sectional view of a preferred embodiment of a active center installed on a cylindrical grinding machine taken along line 8-8 of FIG. 2.
  • FIG. 9 is a cross sectional view of a preferred embodiment of an active center installed on a cylindrical grinding machine taken along line 9-9 of FIG. 2.
  • FIG. 1 an active center apparatus for sensing and compensating for undesirable forces, indicated generally at 10 of the present invention, is shown with a material removing tool, in this case a grinding wheel 12.
  • a material removing tool in this case a grinding wheel 12.
  • FIG. 2 a portion of the apparatus, again indicated at 10, is shown with a material removing machine, in this case a cylindrical grinding machine 14.
  • the cylindrical grinding machine has a headstock 16 and a tailstock or footstock 18, between which a workpiece 20 is disposed for receiving a surface treatment by the grinding wheel 12.
  • the workpiece 20 is actually held between a headstock center and a tailstock center, each disposed in bores formed in the headstock and tailstock, respectively.
  • the conventional centers are elongated cylindrical/conical bodies with a tip for supporting the workpiece. The shape and size of the center bodies are standard. Because these conventional centers are little more than a pointed steel rod, they are referred to as "dead" centers.
  • the grinding wheel 12 is rotatably mounted to a spindle 22, which in turn is connected to a motor 24.
  • the grinding wheel 12 and spindle 22 form an assembly which is moved with respect to the workpiece 20 by hydraulic cylinders
  • the headstock 16 rotates with the workpiece 20 and is connected to a motor 26.
  • the tailstock 18 is adjustably positioned with respect to the head stock 16 to accommodate workpieces of various lengths.
  • the grinding wheel 12 typically rotates at high speed, around 1500 rpm, with respect to the workpiece. Thus, the abrasive surface of the grinding wheel 12 removes material from the surface of the workpiece 20 to produce a desired surface finish.
  • the headstock 16 rotates the workpiece 20 at low speed, around 240 rpm, with respect to the grinding wheel to expose the entire circumference of the workpiece to the grinding wheel.
  • the apparatus 10 of the present invention includes a pair of active centers, a headstock center 30 and a tailstock center 32.
  • the active centers 30 and 32 advantageously have the same standard shape and standard size of the conventional centers.
  • the centers 30 and 32 may be received within the standard headstock 16 and tailstock 18 of conventional cylindrical grinding machines. Therefore, the centers of the present invention may be easily and quickly installed on existing machines in order to retro-fit the machines for the force sensing and compensating apparatus. There is no need to custom design fixtures or other elements to accommodate movement of different wheel/spindle assemblies or headstock and tailstock assemblies.
  • the centers of the present invention fit within existing machines without interfering with the work space or machine components.
  • each center, indicated at 30, has a similar construction including an elongated cylindrical/conical body 34, which has a standard shape and size to fit in conventional headstocks and tailstocks. As shown in the figures, a cylindrical cover 35, as shown in FIG. 9, has been removed from the body to expose the internal components of the center.
  • the body 34 has a pointed, conical tip 36 for inserting in an indentation on the end of the workpiece to support the workpiece.
  • each center 30 and 32 advantageously has an embedded shear load sensor 40 and 42 respectively, disposed generally near the tip 36 of the body 34.
  • the shear load sensor 40 is a well known device that is selected to be as small and thin as possible so as not to interfere with the operation of the centers.
  • the sensor 40 fits generally within the conical envelope of the tip 36.
  • the sensor 40 is a structural element mounted between the tip 36 and the body 34. Forces generated between the workpiece and the grinding wheel or other cutting tool are transferred to the tip 36, through the sensor 40 where they are sensed and transformed in to proportional electrical signals, and into the body 34 of the center 30.
  • the shear load sensor is relatively stiff with respect to the surrounding mechanisms so that its presence does not significantly influence the forces it is measuring, or change the overall deflections of the system. Because the shear load sensors 40 and 42 are imbedded in the centers 30 and 32, they do not interfere with the work space and do not require custom fixtures, such as tables.
  • the shear load sensors 40 and 42 advantageously sense force levels and vibrational frequencies developed between the grinding wheel 12 and the workpiece 20.
  • the sensors 40 and 42 develop signals which are received by a control module 44.
  • the signals may pass through signal conditioning 46 and a low pass filter 48 before being received by the control module 44.
  • a determination may be made as to which force levels and vibrational frequencies are undesirable.
  • Undesirable forces and vibrational frequencies are those which deviate from the most efficient conditions.
  • the precise nature of the most efficient conditions may vary with tool type, workpiece material, and other conditions specific to each situation.
  • the most efficient conditions may be the subject of theoretical analysis, or may be arrived at by purely trial-and-error methods.
  • a tachometer 50 may be disposed adjacent the workpiece 20 to measure the rotational rate of the workpiece.
  • the tachometer develops a reference signal which is received by the controller 44. Because the surface contour of the workpiece repetitively contacts the cutting tool with each revolution, control algorithms may use this information gathered from the tachometer for synchronization.
  • the centers, indicated at 30, advantageously have an imbedded actuator, indicated at 60, to compensate for force and displacement between the workpiece 20 and the grinding wheel 12 (FIGs. 1 and 2).
  • the actuator 60 is preferably a pair of piezoelectric stacks 62 and 64 disposed on opposing sides of the body.
  • a pair of notches 66 and 68 are formed on opposing sides of the center body 34 for receiving the stacks 62 and 64.
  • a generally planar web 70 is formed between the notches 66 and 68 and is collinear with a longitudinal axis 72 of the body 34.
  • Each notch 66 and 68 has a forward wall 74 and 76, a rearward wall 78 and 80, and an inner wall 82 and 84. The portion of the body 34 between the inner walls 82 and 84 of the notches 66 and 68 form the web 70.
  • the piezoelectric stacks 62 and 64 are disposed in the notches 66 and 68, respectively.
  • the piezoelectric stacks 62 and 64 extend between the forward walls 74 and 76 and the rearward walls 78 and 80 of the notches 66 and 68, respectively.
  • Contact bearings 88 typically cylindrical, may be disposed between the piezoelectric stacks 62 and 64 and the forward and rearward walls 74, 76, 78, and 80.
  • Wires 90 are electrically connected to the piezoelectric stacks 62 and 64 and extend from the stacks, through a bore 92, and out an end 94 of the body 34. An electrical signal is applied to the piezoelectric stacks 62 and 64 causing them to expand and contract.
  • the piezoelectric elements 62 and 64 expand they exert a linear force, illustrated by arrows 96 and 98 (FIG. 5), between the forward walls 74 and 76 and rearward walls 78 and 80, respectively.
  • the force exerted by the piezoelectric stacks is generally parallel to the longitudinal axis 72 of the center.
  • the stacks 62 and 64 are disposed on opposing sides of the center body 34, off-set from the longitudinal axis 72.
  • the centers 30 and 32 (FIG. l)are disposed in the headstock 16 and the tailstock 18 respectively (FIG. 1) , they are fixed.
  • the tip 36 of the center 30 bends about the web 70 and displaces laterally, as illustrated by arrow 100 in
  • the piezoelectric stacks 62 and 64 cause the tip 36 to laterally displace 100 and exert a lateral force on the workpiece, and thus the grinding wheel .
  • the piezoelectric stacks represented by 62, include a plurality of piezoelectric elements or actuator layers 110. Each piezoelectric layer 110 responds to the electrical signal supplied through the wires 90 (FIGs. 3 and 4).
  • Each piezoelectric element or layer 110 is generally circular, causing the piezoelectric stack 62 to be generally cylindrical.
  • each layer 114 may be generally semi-circular, causing the stack 116 to be semi-cylindrical, as shown in FIG. 7.
  • the stack 62 may include a piezoelectric sensor or sensor layer 112.
  • the sensor layer 112 develops a signal which is sent through a wire 118 to the controller as shown in FIG 4. The forces can be monitored by monitoring the voltage generated by the sensor layer.
  • the active centers 30 and 32 have been described with reference to piezoelectric actuators, it is of course understood that the actuators may be any type of actuator, such as hydraulic, pneumatic, solenoid, magnetrostriction, etc.
  • the tailstock center 32 is shown disposed in the tailstock 18.
  • the longitudinal axis 72 of the center 32, and of the workpiece 20, and an axis (not shown) of the grinding wheel 12 form a line of centers 130, or a line passing through both axes, as shown in FIG. 8.
  • the tailstock center 32 is oriented such that the web 70 is generally perpendicular to the line of centers 130, as shown in FIG. 8.
  • axis 132 and 134 of the piezoelectric stacks 62 and 64 respectively, lay in the plane of the line of centers 130.
  • the actuators 62 and 64 cause the tip 36 (FIG.
  • the actuators cause the center to apply a force toward or away from the grinding wheel, again as shown by arrow 136.
  • the headstock center 30 is similarly oriented.
  • the actuator 60 of the headstock center 30 and the actuator 60 of the tailstock center 32 are responsive to first and second control signals, respectively.
  • the control signals are developed by and supplied to the actuators 60 by the controller 44.
  • the first control signal may pass through a low pass filter 120 and a high voltage power amplifier 122 and the second control signal may similarly pass through a low pass filter 124 and a high voltage power amplifier 126.
  • the controller 44 monitors the cylindrical grinding machine characteristics and compensates for changes in the speed of the workpiece 20 or the grinding wheel 12, grinding wheels of different diameters, and workpieces with different diameters and masses. In addition, any other conditions that deviate from the ideal conditions may be compensated for.
  • the controller provides for calibrating the grinding machine set-up and for adjusting performance characteristics. Through the active centers, the controller actively controls the grinding process for better surface finishes and lower cycle times.
  • the signal waveform sent to one piezoelectric stack 62 may be phase inverted or 180 degrees phase shifted from the other stack 64, as represented at 128 and 130. Thus, one stack 62 expands while the other 64 contracts to displace the tip 36 (not shown) and apply a lateral force.
  • the control signal waveform developed by the controller 44 may be, or may be converted to, an AC voltage waveform. An AC voltage waveform is preferable for active force control. Alternatively, the control signal may be, or may be converted to, a DC voltage. A DC voltage may be applied to the actuator, or piezoelectric stacks, to cause a known displacement of the tips 36, and thus the workpiece 20 toward or away from the grinding wheel 12.
  • a DC voltage advantageously may be applied to both centers 30 and 32 to cause the workpiece to be rapidly removed from the grinding wheel.
  • the workpiece may be rapidly withdrawn from the grinding wheel, as opposed to slowly moving the grinding wheel/spindle assembly away as conventionally done. Rapidly removing the workpiece results in a better surface finish and lower cycle time, and thus higher through-put.
  • a DC voltage advantageously may be applied to one of the centers to move one end of the workpiece towards or away from the grinding wheel.
  • any misalignment between the workpiece and the grinding wheel may be corrected by laterally displacing the tip of the center, as opposed to manually correcting for machine misalignment as conventionally done. Adjusting the misalignment by laterally displacing the tip of the center results in lower cycle time and thus higher through-put.
  • the active centering apparatus of the present invention has been described with respect to compensating for undesirable conditions including undesirable force levels and vibrational frequencies.
  • the apparatus of the present invention may be used to impart a contoured shape into the workpiece.
  • a contoured surface may be impossible, or at least very difficult, to achieve by traditional means.
  • the contoured surface may be used as longitudinal bearing raceways or to create keyed fits of parts into similarly contoured holes.
  • Such contoured surfaces may be shaped as multi-pointed star patterns or rectangles when viewed in cross- section.
  • the centers of the present invention have imbedded sensors for sensing force levels and vibrational frequencies and because they have imbedded piezoelectric actuators to compensate for force and displacement, they are referred to as "active" centers, as opposed to the "dead” centers of the prior art. It is of course understood that although the centers of the present invention have been described and illustrated as having both imbedded sensors and imbedded actuators, the centers may have only a sensor or an actuator. In addition, although the present invention has been described and illustrated with respect to centers for cylindrical grinding machines, it is of course understood that other types of machines and other types of workpiece holders may be imbedded with sensors and/or actuators in accordance with the principles of the present invention.

Abstract

Dispositif servant à capter et à corriger des niveaux de force et des fréquences vibratoires dans une machine à meuler possédant des centres actifs. Ces centres actifs possèdent des capteurs de charge de cisaillement encastrés et des organes de commande encastrés. Ces capteurs permettent d'obtenir des informations en temps réel concernant le meulage et de déterminer des niveaux de force indésirables, ainsi que des fréquences vibratoires. Les organes de commande consistent en une paire d'empilements piézo-électriques situés sur les côtés opposés du corps central dans des échancrures. Une tension appliquée par une unité de commande provoque l'expansion et la contraction de ces empilements piézo-électriques. L'action exercée par les empilements piézo-électriques provoque le déplacement latéral de la pointe du centre et l'application d'une force latérale à la pièce. On peut appliquer un signal de tension de courant alternatif afin de commander la force. On peut appliquer un signal de tension de courant continu pour le déplacement, afin, par exemple, d'éloigner rapidement la pièce de la meule ou de corriger le défaut d'alignement entre la pièce et la meule. Etant donné que les capteurs et les organes de commande sont encastrés, ils n'exercent aucun effet sur l'espace de travail ou sur les éléments de la machine. De plus, ces capteurs et ces organes de commande sont fabriqués en dimensions standard, de sorte que les centres actifs peuvent moderniser sans difficultés des machines existantes.
PCT/US1998/023112 1997-11-25 1998-10-29 Dispositif de centrage actif possedant un capteur de charge de cisaillement et un organe de commande encastres WO1999026755A2 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU12073/99A AU1207399A (en) 1997-11-25 1998-10-29 Active centering apparatus with imbedded shear load sensor and actuator

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US08/977,791 US5938503A (en) 1997-11-25 1997-11-25 Active centering apparatus with imbedded shear load sensor and actuator
US08/977,791 1997-11-25

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WO1999026755A2 true WO1999026755A2 (fr) 1999-06-03
WO1999026755A3 WO1999026755A3 (fr) 1999-07-15

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WO2015097146A3 (fr) * 2013-12-23 2015-08-13 Hydro Aluminium Rolled Products Gmbh Dispositif de rectification de cylindre et procédé de rectification d'un cylindre
CN105848826A (zh) * 2013-12-23 2016-08-10 海德鲁铝业钢材有限公司 辊磨设备和用于磨削轧辊的方法
CN105848826B (zh) * 2013-12-23 2018-04-13 海德鲁铝业钢材有限公司 辊磨设备和用于磨削轧辊的方法

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US5938503A (en) 1999-08-17
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